WO2017087638A1 - Vanne à autorégulation basse pression et basse énergie - Google Patents
Vanne à autorégulation basse pression et basse énergie Download PDFInfo
- Publication number
- WO2017087638A1 WO2017087638A1 PCT/US2016/062474 US2016062474W WO2017087638A1 WO 2017087638 A1 WO2017087638 A1 WO 2017087638A1 US 2016062474 W US2016062474 W US 2016062474W WO 2017087638 A1 WO2017087638 A1 WO 2017087638A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- pressure
- flow
- flow rate
- tube
- self
- Prior art date
Links
Classifications
-
- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
- G05D7/00—Control of flow
- G05D7/01—Control of flow without auxiliary power
- G05D7/0106—Control of flow without auxiliary power the sensing element being a flexible member, e.g. bellows, diaphragm, capsule
- G05D7/0113—Control of flow without auxiliary power the sensing element being a flexible member, e.g. bellows, diaphragm, capsule the sensing element acting as a valve
-
- A—HUMAN NECESSITIES
- A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
- A01G—HORTICULTURE; CULTIVATION OF VEGETABLES, FLOWERS, RICE, FRUIT, VINES, HOPS OR SEAWEED; FORESTRY; WATERING
- A01G25/00—Watering gardens, fields, sports grounds or the like
- A01G25/02—Watering arrangements located above the soil which make use of perforated pipe-lines or pipe-lines with dispensing fittings, e.g. for drip irrigation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
- F16L55/00—Devices or appurtenances for use in, or in connection with, pipes or pipe systems
- F16L55/04—Devices damping pulsations or vibrations in fluids
- F16L55/045—Devices damping pulsations or vibrations in fluids specially adapted to prevent or minimise the effects of water hammer
- F16L55/05—Buffers therefor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
- F16L55/00—Devices or appurtenances for use in, or in connection with, pipes or pipe systems
- F16L55/04—Devices damping pulsations or vibrations in fluids
- F16L55/045—Devices damping pulsations or vibrations in fluids specially adapted to prevent or minimise the effects of water hammer
- F16L55/055—Valves therefor
Definitions
- This invention relates to a self-regulating valve allowing independent control of flow rate and activation pressure for use in an irrigation system.
- Drip irrigation is a means of reducing the water required to irrigate by up to 60%, and it has been shown to be a successful development strategy enabling poor farmers to rise out of poverty by growing more and higher value crops.
- the barrier to drip irrigation achieving large-scale dissemination is the cost of the pump and power system.
- the power consumption is equal to the product of flow rate and pressure. For a given farm, the flow rate is
- the primary opportunity to reduce the power consumption is to lower pumping pressure.
- Pressure compensation is a means of maintaining a constant flow rate from a drip emitter under varying applied pressure - an important feature for a low pressure dripper network where pressure from the pump to the end of the line can vary by a factor of three.
- the self-regulating valve of the invention includes a static pressure chamber and an elastically collapsible tube supported within the static pressure chamber.
- static pressure is meant a fluid maintained at a selected static pressure in the chamber.
- a flow restrictor is in fluid communication with the collapsible tube inside the static pressure chamber and piping is provided connecting a source of pressurized liquid both to the flow restrictor and to an opening into the static pressure chamber, whereby flow rate through the valve remains substantially constant with variations in pressure of the pressurized liquid.
- the flow restrictor is a needle valve.
- Fig. 1 is a graph of flow rate against driving pressure illustrating the activation pressure.
- Fig. 2a is a cross-sectional view of a prior art Starling resistor.
- Fig. 2b is a cross-sectional, schematic illustration of an improved Starling resistor architecture as disclosed herein.
- Figs. 3a and 3b are graphs of flow rate against pressure.
- Fig. 4a is a graph of k v versus flow rate.
- Fig. 4b is a graph of flow rate against pressure showing that changing resistance of the needle valve allows for control of the flow rate independent of the activation pressure.
- Fig. 5a is a graph of flow rate against pressure for an embodiment of the invention.
- Fig. 5b is a graph of flow rate versus pressure with variations in a tube property such as tube wall thickness.
- Figs. 6a and 6b are graphs of flow rate against pressure for tube length variations.
- Fig. 7a is a graph showing a comparison of activation pressures from experimental results and from theory.
- Fig 7b is a graph comparing limited flow rates from experimental results and from theory.
- a novel design of a low-energy, passive self-regulating pressure compensating valve with a single pressure source is disclosed for drip irrigation.
- Pressure compensation is a mechanism that sustains a flow at constant flow rate regardless of the driving pressure.
- the minimum driving pressure that initiates the pressure compensation is called the "activation pressure" (Fig. 1).
- Activation pressure is key to pumping power - since the power is proportional to the product of flow rate and pressure, the activation pressure dictates the minimum maintaining pressure of the system and thus determines the lowest pumping power, given a fixed flow rate.
- this design can reach an extremely low activation pressure using a flexible tube architecture.
- a Starling resistor is a device consisting of an elastically collapsible tube mounted inside a static pressure chamber as shown in Fig. 2a [1].
- the experimental setup included a pressure supply, a measurement system and a modified Starling resistor (Fig. 2b).
- the whole system was driven by static pressure from a pressure tank, which was pressurized by compressed air and controlled by a pressure regulator.
- the pressure could range from 0 to 200 kPa (0 - 2 bar).
- the pressure tank was connected to the Starling resistor 10 through a high-resolution rotor flow meter 12
- a branch was installed downstream of the flowmeter to pressurize the Starling resistor 10 chamber and a pressure transducer 14 (Setra model 209 with a measurement range of 0-172 kPa) was installed at the branch to monitor the pressure. Since the water could be treated as static in the branch and in the chamber, the measurement of the transducer was equal to the pressure at the T-junction point at the beginning of the branch, which was also equal to the pressure in the chamber.
- the pressure transducer and the flow meter were connected to a data logger to record the real-time signal with a sampling rate of 2000 Hz.
- the flow limitation results are presented in terms of flow rate versus driving pressure.
- the pressure is the reading from the pressure transducer 14 and represents the pressure difference from the pressure chamber to the atmosphere.
- the pressure difference from the end of the unsupported section to the outlet is negligible compared to the pressure change along the unsupported section, so the pressure measurement from the transducer can be considered as the transmural pressure applied at the end of the unsupported tube.
- Two flow limitation modes are found and shown in Figs. 3a and 3b.
- the results in the figure are original data for a single trial. Each result includes two curves: the solid curve was obtained in the pressurizing scenario, and the dash line is from the depressurizing scenario.
- the pressure variation process is also shown by the arrows in the figure. The difference between them is due to the hysteresis stemming from the nonlinear tube deformation and the nonlinear flow dynamics.
- Mode 2 in Fig. 3b is more complex, and was found in Cases C and D. Similar to Mode 1 , the flow rate initially increased with the square root of the pressure until reaching P a , with no deformation in the tube cross-section. After the peak, the flow rate dropped gradually, while the tube was steadily squeezed and the cross-sectional area decreased until the flow dropped to the lower limit of the flow meter. In the depressurizing scenario, the flow rate increased abruptly and overshot the pressurizing scenario. The difference in flow rate depended on how quickly the pressure was decreased. The flow rate then fell back to the value of the pressurizing scenario when the oscillation decayed. It followed a lower route to reach the zero point due to hysteresis. We observed that the flow limitation behavior was dependent To ensure the
- the present experiment employed a novel way to induce a transmural pressure by introducing a needle valve, rather than a separate external pressure.
- the resistance coefficient of the valve was determined by measuring its flow rate at different driving pressures (Fig. 4a), i.e. ⁇ where P v is the pressure drop over the valve and u v is the mean velocity at the inlet of the valve.
- Fig. 4a driving pressures
- FIG. 4b Another observation about Fig. 4b is that the flexible tube suddenly fully closed at the highest pressure, cutting off the flow. This stopping pressure decreased with smaller valve openings.
- the flow rate had a spike from zero before a flow was initiated, at which point the flexible tube had a sudden opening. The pressure of the spike was also lower than the stopping point due to hysteresis or system bi-stability.
- A is the averaging cross-sectional area
- a 0 is the cross-sectional area before the deformation
- n is the fitting exponent
- ⁇ is the dimensionless transmural pressure.
- the best reported fitting exponent, which captured pressure compensating flow limitation, was n 3/2.
- the pressure loss from the T-junction to the end of the tube in Fig. 2 is contributed by two components: the resistance of the needle valve and the flexible tube. The pressure loss can be described by
- u v and A v are the flow velocity and the cross-sectional area inside the needle valve
- u is the average velocity in the flexible tube
- k v is the pressure loss coefficient of the needle valve
- k t is the pressure loss coefficient incurred by the flexible tube.
- the cross-sectional area ratio can be estimated by .
- In mode 1 (for small
- a 0 A v and the flexible tube remains circular in shape at the steady state, so A * A 0 ; in mode 2 (for big diameter tubes), A 0 - 4A V and a significant collapse was observed such that A ⁇ A 0 . Therefore,
- a modified Starling resistor is disclosed to design a passive, self-regulating valve.
- a needle valve was introduced in the traditional Starling resistor allowing the flow rate and activation pressure to be controlled separately.
- the flow limitation phenomenon can be used to self-regulate the flow rate with a very low pumping pressure.
- a lumped-parameter model was developed to capture the magnitude and trend of the flow limitation observed in experiments at various tube geometries. The trend and magnitude of the experimental results are well predicted by the lumped parameter model.
- the new architecture disclosed herein is able to control separately the activation pressure and flow rate through the needle valve.
- the tube geometry determines the activation pressure and the needle valve or flow restrictor determines the flow rate.
- Experiments were performed to quantify the needle valve's effect and a parametric investigation of tube geometry on flow limitation was performed to clarify the mechanism to adjust the activation pressure.
- the examined factors include inner diameter, length and wall thickness of the elastic tube.
- a lumped-parameter model captures the magnitude and trend of the flow limitation.
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- Physics & Mathematics (AREA)
- General Physics & Mathematics (AREA)
- Engineering & Computer Science (AREA)
- Automation & Control Theory (AREA)
- Infusion, Injection, And Reservoir Apparatuses (AREA)
Abstract
L'invention concerne une vanne à autorégulation. La vanne comprend une chambre de pression statique avec un tube déformable élastiquement soutenu dans la chambre de pression statique. Un restricteur est en communication fluidique avec une entrée dans la chambre de pression statique pour un écoulement par le tube déformable. Une tuyauterie relie une source de liquide sous pression, à la fois vers le restricteur et vers une ouverture dans la chambre de pression statique, moyennant quoi le débit dans la vanne reste sensiblement constant avec des variations de pression du liquide sous pression. Dans un mode de réalisation préféré, le restricteur est une soupape à pointeau.
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US15/320,877 US10254770B2 (en) | 2015-11-20 | 2016-11-17 | Low-pressure and low-energy self-regulating valve |
US16/376,574 US10761545B2 (en) | 2015-11-20 | 2019-04-05 | Low-pressure and low-energy self-regulating valve |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US201562257937P | 2015-11-20 | 2015-11-20 | |
US62/257,937 | 2015-11-20 |
Related Child Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US15/320,877 A-371-Of-International US10254770B2 (en) | 2015-11-20 | 2016-11-17 | Low-pressure and low-energy self-regulating valve |
US16/376,574 Continuation US10761545B2 (en) | 2015-11-20 | 2019-04-05 | Low-pressure and low-energy self-regulating valve |
Publications (1)
Publication Number | Publication Date |
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WO2017087638A1 true WO2017087638A1 (fr) | 2017-05-26 |
Family
ID=58717824
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/US2016/062474 WO2017087638A1 (fr) | 2015-11-20 | 2016-11-17 | Vanne à autorégulation basse pression et basse énergie |
Country Status (2)
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US (2) | US10254770B2 (fr) |
WO (1) | WO2017087638A1 (fr) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10761545B2 (en) | 2015-11-20 | 2020-09-01 | Massachusetts Institute Of Technology | Low-pressure and low-energy self-regulating valve |
CN114060642A (zh) * | 2022-01-12 | 2022-02-18 | 艾肯(江苏)工业技术有限公司 | 一种上水管路用的具有柔性密封结构防水锤装置 |
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Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10761545B2 (en) | 2015-11-20 | 2020-09-01 | Massachusetts Institute Of Technology | Low-pressure and low-energy self-regulating valve |
CN114060642A (zh) * | 2022-01-12 | 2022-02-18 | 艾肯(江苏)工业技术有限公司 | 一种上水管路用的具有柔性密封结构防水锤装置 |
CN114060642B (zh) * | 2022-01-12 | 2022-04-01 | 艾肯(江苏)工业技术有限公司 | 一种上水管路用的具有柔性密封结构防水锤装置 |
Also Published As
Publication number | Publication date |
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US10761545B2 (en) | 2020-09-01 |
US10254770B2 (en) | 2019-04-09 |
US20180246530A1 (en) | 2018-08-30 |
US20190332128A1 (en) | 2019-10-31 |
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